Synchronizer coupling



Oct. 17, 1944. ORR 2,360,711

SYNCHRONIZER COUPLING Filed March 24, 1943 I5 Sheets-Sheet 1 Oct. 17, 1944. P. ORR 2,360,711

SYNCHRONIZER COUPLING Filed March 24, 194:5 a Sheets-Sheet 2 Oct. 17, 1944.

P. ORR 2,360,711

SYNCHRONIZER COUPLING Filed March 24, 1945 3 Sheets-Sheet 3 Patented Oct. 17, 1944 SYNCHRONIZER COUPLING Palmer Orr, Muncie, Ind., asslgnor to Borg- Warner Corporation, Chicago, 111., a corporation of Illinois Application March 24, 1943, Serial No. 480,274

6 Claims.

This invention relates to power transmitting devices of the variable type and particularly to a positive coupling combined with such a power transmitting device for controlling the variation in torque produced by the mechanism.

There has been devised a positive coupling device which is supplied with spiral splines so as to take advantage of the relative direction of rotation between the elements to be coupled to effect an axial shift of the movable element thereof. To limit the axial movement of the shlftable element, straight or axial splines are likewise provided on another portion of the shiftable element so that when the shift is completed, the shiftable element is connected to the spirally splined element through a secondary straight splined connection. The last-named connection provides a lock which prevents further axial movement of the shiftable element. To effect a shift in the opposite direction the straight splined connection must first be broken and then the direction of torque is reversed, thereby causing the spirally splined element to move in the opposite direction. In one form, pawls are provided to synchronize the shift, the pawls being so related with respect to the teeth to be mated that when a pawl is in a driving position, the teeth of the clutch will be perfectly aligned and will engage due to the driving action of the pawl on the spirally splined shif ble element.

Thus it will be observe that in the coupling just described two sets of splines are necessary, the first being splralled to provide the necessary axial movement and the second being straight to provide the necessary lock to prevent further movement of the spirally splined element. It will be appreciated that both sets of splines are rather expensive and that it would be desirable to reduce the cost of such a coupling to a minimum. The principal object of this invention, therefore, is to provide a positive coupling of the type described which will eliminate some of the splines and hence result in a less expensive mechanism.

Another object of this invention is to provide a simple and inexpensive lock for a coupling of the type described.

A further object of this invention is to provide a transmission of the stepped-type wherein changes in speed ratio are effected by means of a coupling device having a spirally splined, axially shiftable element and a simple, inexpensive, looking device for the axially shiftable element.

A still further object of this invention is to substitute an inexpensive ball or bean-type lock for the straight-splined lock which has been proposed for this type of coupling.

These and other objects of the invention will become apparent from the following specification when taken together with the drawings which form a part thereof and in which:

Fig. i is a partial elevation in section of a transmission embodying a shifting device constructed in accordance with this invention;

Fig. 2 is a fragmentary section taken along line 22 of Fig. 1;

Fig. 3 is a fragmentary section taken along line 3-3 of Fig. 1;

Fig. 4 is a fragmentary section through the coupling device taken along line 4-4 of Figs. 1 and 5;

Fig. 5 is a fragmentary side elevation in section of the coupling device taken along line 55 of Fig. 4;

Fig. 6 is a fragmentary plan view of the coupling device taken along line 6-4 of Fig. 5;

Fig. 7 is a fragmentary elevation taken along line 'I-l of Fig. 1 showing the detailed construction of the planet carrier;

Fig. 8 is a view similar to Fig. 7 showing the planet carrier prior to assembly;

Fig. 9 is a fragmentary elevation of the controls for the shifting mechanism taken along line 99 of Fig. 10; and

Fig. 10 is a fragmentary section of the shifting mechanism.

Referring to Fig. 1 for a detailed description of the invention, the transmission is enclosed in a housing It and serves to connect a drive shaft shown at it, to a driven shaft l1. Drive shaft Hi may be the crank shaft of an airplane engine and driven shaft i'l may be the propeller shaft although it will be understood that the invention is not limited to such use. The transmission itself is designated by reference character l8 and is comprised of a sun gear l9 bolted to drive shaft i6, pairs of planet pinions 20 and 2| made in the form of spools so as to be rotatable together and mounted on planet shafts 26 in a carrier 22 which is rotatable about the axis of shaft ll. Sun gear I! engages planet pinion 20 and planet pinion it engages a larger sun gear 23 which is splined to shaft l1 and thus caused to be rotatable therewith. Carrier 22 includes a front ring 24 and a rear ring 25 in which planet shafts 28 are retained.

Referring to Figs. 7 and 8, planet carrier 22 is provided with axially extending bars 21 which pass between the planet gears and which are provided with grooves 28 on the interior thereof.

Cooperating with grooves 2! are lugs 28 which are formed in a radial flange III of a bushing II. Said bushing II is mounted on the inside of sun gear II and provides a support for the carrier.

As shown in Fig. 8, lugs 28 are assembled with respect to bars 21 by first assembling the planets and cage around the lugs 28 so that said lugs extend into the space between the planet gears 20 and ii and then the radial flange is rotated relative to bars 21 until the two assume a position as shown in Fig. 7. A notch 32 is provided in one of the lugs 29, said notch being adapted to cooperate with the reduced end II of a set screw 34 which is advanced into the notch so as to prevent the carrier from rotating oil its support. Grooves It fit snugly over lugs II so as to give a flrm support to the entire carrier.

It will be obvious that in order to obtain a reduced drive through the transmission lust described carrier 21 must be held so that the drive is then from drive shaft It to sun gear l8, 128:1

113 Ill and II, and then to sun gear gin i z n gear II is splined to driven shaft II. the latter will be rotated at the same speed as sun gear 23. Due to the difference in size between sun gears l8 and 28, the latter will be rotated at a reduced speed.

To obtain a direct drive between drive shaft l6 and driven shaft ll, one of the sun gears must be connected to the planet cage so as to lock the entire planetary gear set together for rotation as a single unit. The means by which the two ratios are obtained will now be described.

Carrier 22 is provided with a cylindrical flange 35 which may be an extension of front ring 24. This flange is axially fixed, but is rotatable with planet carrier 12. On the inside of flange 35 are internal splines Ii, the direction of the spiral being shown in Fig. 6. It is assumed that the direction of rotation of drive shaft i I is clockwise when the transmission is viewed from the righthand side of Fig. 1.

Sun gear 23 is provided with external teeth 31 which are of the straight axial type.

Secured to housing It is an internally toothed ring 88, the teeth being shown at I9. It will be noted that external teeth 31 on sun gear 23 are located within the cylindrical flange 35 on carrier 22 and that internal teeth I9 on ring 38 are substantially aligned with flange 35. In order to eifect a connection between flange 3i and stationary ring SI an axially slidable sleeve 40 is provided. This sleeve is formed with external spiral splines ll which cooperate with internal spiralsplines is on flange 35. and with straight external splines 42 which are separated from the splrals'plines Ii by a circumferential groove 0 and which are adapted to engage internal teeth 39 on fixed member ll.

Similarly, flange Ii may be connected to sun gear II through the intermediary oi internal splines I. external splines ll and internal straight splines located on the inside and to the right of sleeve lll (Fig. 1). It will be noted that straight splines 12 and II are considerably longer-than internal teeth I. and external teeth 31 with which the straight splines are adapted to mesh. As shown in Fig. 1, straight splines 44 are engaged with external teeth 31 so as to form a drive between sun gear a and carrier 22. External splines II are made long enough to engage one or more pawli I mounted on flxed ring 38 (Fig. 2) and held against splines 42 by means of a spring 46. It will be observed that every third spline is 0! normal size and the two intervening splines are of reduced height so as to permit pawls 45 to bear against the normal splines to obtain a drive therefrom.

In a similar manner, when sleeve 40 is engaged with internal splines Ill on fixed ring 38, internal splines 44 on sleeve 40 will be completely disengaged irom external splines 31 on sun gear 2!, but they are made sulllciently long so as to remain in engagement with a pawl 41 pivotally mounted on sun gear 23 and held against the internal splines 44 by means or a spring 48. Internal splines H are likewise formed of uneven height so that every third spline is of normal height and the intervening two splines are of reduced height, thus permitting pawl 41 to engage the splines of normal height Assuming that sleeve 40 is free to move axially in either direction, it is apparent that a shift to reduced drive may be eifected by accelerating shaft it while permitting shaft II to rotate at substantially the same speed. Eventually, sleeve Ill and carrier 22 will stop and begin to rotate in the opposite direction and at such time pawl 45 will cease to ratchet over splines 42 and will engage a spline or normal height thereby preventing sleeve 40 irom continuing to rotate with flange I5. This establishes a speed diflferential between sleeve I and flange 35 which, because of the spiral spline connection therebetween, results in an axial movement of sleeve 40 toward internal splines Ill. The length and position of pawl 46 are so chosen that splines 42 under such conditions are perfectly aligned with internal splines 39 and complete engagement may be eifected without diflicuity.

Assuming external splines 42 to be engaged with internal splines 39 and sleeve Iii to be free to move axially. pawl 41 on sun gear 23 is in engagement with internal splines 44 at the opposite end of sleeve 40 and is ready to take eflect Just as soon as the direction of rotation is reversed. Thus, when torque is released to decelerate shaft Ii. the relative direction of rotation between sleeve I and flange 35 is reversed and pawl 41 then takes hold and causes sleeve I to move to the right as shown in Fig. l. Pawl 41 is likewise so positioned that when it is in engagement with the normal sized internal splines 4|, the splines will likewise be in perfect alignment with external teeth TI and the movement of sleeve an to the right as shown in Fig. i will continue until complete engagement between external teeth 31 and internal splines I is elected.

It is obvious that unless some locking means is provided for sleeve I, the sleeve will continue to oscillate between engagement with internal splines 30 and external teeth 31 with each reversal of torque between the driving and driven shafts. To maintain sleeve I in any given positlon, therefore. requires that some locking means be provided. Such locking means will now be described.

It will be observed that axial flange I5 is provided with an opening I! in which is located a locking member 60. In the form selected for illustration the locking member is comprised of a ball, but it is understood that any of the usual interlocking devices with cammed ends may be used. Said member has a diameter which is greater than the thickness of flange 35 and is adapted to ride in either one of two depressions II and I2 located in sliding sleeve 40. To reduce any tendency toward self-locking and also to provide a faster and more dependable shift, the splines between depressions and 52 are reiieved as shown at 14. Surrounding flange 35 is a shift collar 53 which is likewise provided with a depression 55. Thus when depression 55 and depression 51 or 52 are in alignment, movement of sleeve 45 axially is possible, but when depression 54 is not aligned with depression 5| or depression 52, the ball 55 locks sleeve 55 in place. Thus, when it is desired to shift from the position shown in Fig. 1 to the position wherein carrier 22 is held, collar 53 is slid to the left as shown in Fig. 1 until depression 54 is aligned with depression 5| and then, assuming that the torque reaction is in the proper direction, sleeve 45 will move to the left to engage external splines 42 with internal teeth 35. To lock sleeve 45 in this position it is necessary to continue moving shift collar 53 to the left immediately after ball 55 drops into depression 52. Similarly, when it is desired to lock sleeve 45 in the position shown in Fig. 1 from the position just described, it is necessary first to move shift collar 53 so that depression 54 is in line with depression 52 and then, assuming that the torque reaction is in the proper direction, sleeve 55 will move to the right into the position shown in Fig. 1 and immediately upon ball 55 dropping into depression 5|, collar 53 must be moved to the position shown in Fig. 1.

To make sure that shift collar 53 pauses when depression 54 is aligned with either depression 5| or depression 52 to give ball 55 an opportunity to be cammed out of the way of sleeve 55, the device shown in Figs. 4, 5, and 6 is used.

Referring now to Figs. 4, 5, and 6, flange 35 has formed therein one or more axial slots 55. Slot 55 is located in the region over which shift collar 53 operates. Said colla 53 is provided with a radial pin 55 which is flattened along its sides as at 51 so as to pass through slot 55 without turning. Similarly, sleeve 45 is provided with a somewhat rectangular slot 55 which is considerably wider than pin 55 and into which said pin 55 extends. Since sleeve 55 and flange 35 are connected together by means of spiral splines, it will be apparent that sleeve 45 will at times move circumferentially with respect to flange 35 and it is to accommodate the relative circumferential movement between these two parts that slot 55 is made wider.

The axial length and location of slot 53 is so chosen that, assuming sleeve 45 to be in the position shown in Fig. 1, shift collar 53 will move axially until pin 55 strikes the lefthand (Fig. 5) side of slot 55, and it is at exactly this point that depression 54 in collar 53 ball 55 and depression 5| 53, therefore, must pause in its axial movement until the torque reaction moves shift sleeve 35 into engagement with internal teeth 35, that is, until the shift sleeve passes from one extreme position to its other extreme position. At that time, collar 53 may then continue its movement a short distance so as to lock ball 55 and sleeve 45 in place. The same action takes place when the movement is from engagement with internal teeth 35 to engagement with external teeth 31 and sun gear 23.

The means by which shift collar 53 is moved in either direction is shown in Figs. 9 and 10. Shift collar 53 is provided with a circumferential groove 59 in which is located a shift yoke 55. Said shift yoke is pivotally mounted at 1| in an arm 5| which in turn is mounted to rotate freely about a control shaft 52. Said control shaft is rotatably mounted in a boss 53 in housing in sleeve 55. Collar will be aligned with axial movement by means of a threaded pin 54. Shaft 52 may be oscillated from the exterior by means of a lever 55. The inner end of shaft 52 is ground to provide one or more fiat spots 55 which serve to drive a lever 55. Said lever 55 is forked at its free end to receive a tongue 51 secured to a hollow cylinder 58. Said tongue 51 is held in the forked end of lever 55 by means of a pin 55 about which it freely pivots. Shift fork 55 is provided with an extension 15 located concentrically with respect to pivot 1| of lever 55 and a hollow cylinder 12 is pivotally mounted about extension 15. Hollow cylinde 12 telescopes into cylinder 53 and a spring 13 is compressed in cylinder 12 so as to tend to cause cylinder 12 and cylinder 55 to spread apart.

When it is desired to shift collar 53, external lever 55 is thrown to the side which will effect the desired shift, the lever being limited in its move ment by a suitable stop (not shown). since the length of lever 55 plus the length of cylinder 12 when extended, is greater than the length of lever 5|, spring 13 will be compressed and will exert a turning effort on lever 5| in the opposite directionto that imparted to lever 55. Shift fork 55 and collar 53 will then move in the desired direction under the action of the spring 13 until pin 55 strikes one end or the other of slot 55, whereupon a pause will be effected until sleeve 45 is unlocked and moved to its other position. When the second depression in sleeve 45 is aligned with ball 55 so as to unlock collar 53, the spring 13 will then continue the movement of shift collar 53, thereby locking sleeve 55 in place.

It is understood that several locking bolts may be used as desired, and likewise several pins 55 and associated slots may be used to secure greater efiectiveness of both devices and a bette balance. It is understood further that although the locking means for shift sleeve 55 is shown as applied to a particular form of shift sleeve and a particular type of gearing, it is not necessarily limited to such a disclosure and that the scope of the invention, therefore, should be determined only by the appended claims.

I claim:

1. A coupling for machine elements adapted to change their relative direction of rotation, comprising spaced elements to be coupled, a member for establishing a connection between the elements, means responsive to a change in the relative direction of rotation of the machine elements for moving the member to or from a coupling establishing position, means for rendering the member independent of changes in relative direction of rotation, said last-mentioned means comprising a bolt movable into and out of the path of movement of the connecting member to stop or to permit movement of the connecting member, and means for controlling the position of the bolt, said osition-controlling means comprising a shiftable element having a depression therein to receive the bolt when the bolt is moved out of the path of movement of the connecting member, resilient means for moving the shiftable member from a position wherein the depression is not aligned with the bolt to a position wherein the depression is aligned with the bolt and thence to a third position wherein the depression again is not aligned with the bolt, means for biasing the spring to effect such movement of the shiftable element and means for arresting the movement of the shiftable element in the position wherein the depression is aligned with the bolt 15 and is held against carrier for the planet pinions. means for arrestin: the rotation of the carrier and for connecting the carrier to a sun ge said connecting means being productive oi axial thrusts, and means ior supporting the carrier from one or the shafts and for taking a portion of the end thrusts. said lastmentioned means comprising a sleeve supported by and abutting said one of the shafts, and a radial flange on the sleeve passing between the pin-net gears, said carrier having close fitting grooves for receiving the tense. whereby to support the carrier from the flange.

8. Planetary gearing as described in claim 2. the sleeve-s pporting shaft being hollow and said sleeve being mounted within the hollow portion of said short.

4. A coupling for machine elements adapted to change their relative direction oi rotation comto change their relative direction or rotation lishing position, and means for rendating the member independent or change in relative direction oi rotation. ing a bolt member change their relative direction oi. rotation. commovement 0! said member, spring means for moving the ring from a. position wherein the depression therein is on one side 01' the bolt. to a second position wherein the depression is aligned and thence to PALMER. ORR. 

